Abstract:

The invention relates to a hinge actuator comprising a first part which is
configured for connection with a second part via an electric drive. The
first and the second part are provided with stops cooperating in a
pivoting direction for defining a select or predetermined position of the
actuator parts with respect to each other. In an embodiment, in a first
position of a coupling between the first part and the second part, these
parts can pivot via the electric drive. In a second position, the first
part and the second part are not connected via the drive but can be
pivoted relative to each other manually. Further, the first and the
second part may be provided with stops only cooperating in the second
position of the coupling in an opposing pivoting direction, for defining
the select or predetermined position.

Claims:

1. A hinge actuator comprising:a first part including first stops;a second
part including second stops;an electric drive, the first part configured
for connection to the second part via the electric drive; anda coupling
provided between the first and second parts such that in a first position
the first part and the second part are connected via the drive and can be
pivoted relative to each other manually, and in a second position the
first part and the second part are not connected via the drive and can be
pivoted relative to each other manually;wherein the first and second
stops only cooperate in the second position of the coupling in an
opposite pivoting direction and are configured to define a select or
predetermined position, the first and second stops are not active in the
first position of the coupling, and the first and second stops are only
active in the second position of the coupling.

2. The hinge actuator according to claim 1, wherein the first part
comprises a base plate provided with a base shaft, and the second part
comprises a supporting frame extending around the base shaft for
supporting a mirror housing.

3. The hinge actuator according to claim 2, wherein the coupling comprises
a coupling ring, the coupling ring disengagably rotation-coupled with
respect to the base shaft and axially moveable between the first position
and the second position.

4. The hinge actuator according to claim 1, wherein the first stops and
second stops are configured in the opposite pivoting direction so that
occurring reaction forces associated with their cooperation are in the
same order of magnitude as occurring reaction forces associated with
their cooperation in the pivoting direction.

5. The hinge actuator according to claim 1, further comprising a
switch-off mechanism for switching off the electric drive, wherein the
force for overcoming the first stops is at least the same order of
magnitude as the force at which the drive is switched off by the
switch-off mechanism.

6. The hinge actuator according to claim 5, wherein the switch-off
mechanism comprises a current limiting circuit, and the electric current
of the circuit for overcoming the first stops is at least the same order
of magnitude as the current at which the current limiting circuit
switches off the drive.

7. The hinge actuator according to claim 2, wherein the second stops are
formed by a cam that is configured or arranged on the supporting frame
for traversing a path during pivoting of the supporting frame, and at
least one first stop positioned fixedly with respect to the base shaft;
and further wherein a first pair of butting faces of a first cam track,
the first pair of butting faces positioned fixedly with respect to the
base shaft, and wherein the first stops are formed by the cam arranged on
the supporting frame and at least one second stop configured or arranged
to be movable with respect to the base shaft.

8. The hinge actuator according to claim 7, wherein the second stop is
configured or arranged to be axially moveable with respect to the base
shaft.

9. The hinge actuator according to claim 3, wherein the coupling ring
comprises a gear wheel configured for engagement with an output part of
the electric drive such that in the first position the gear wheel is
locked against rotation relative to the base shaft, and in the second
position the gear wheel is freely rotatable relative to the base shaft.

10. The hinge actuator according to claim 3, further comprising an
auxiliary coupling ring disposed around or about the base shaft between
the coupling ring and the supporting frame.

11. The hinge actuator according to claim 10, wherein the auxiliary
coupling ring and the supporting frame include auxiliary stops, the
auxiliary stops cooperate in the second position in an opposing pivoting
direction and comprise the first stops.

12. The hinge actuator according to claim 3, further comprising an
intermediate ring disposed around or about the base shaft, the
intermediate ring under axial spring action, wherein in the first
position the intermediate ring is supported on the supporting frame and
in the second position the intermediate ring is supported on the coupling
ring.

13. The hinge actuator according to claim 3, wherein a circumference of
the base shaft includes a two-topped profile, and wherein the coupling
ring includes a cam for cooperation with the two-topped profile.

14. The hinge actuator according to claim 13, wherein in the first
position, the coupling ring in a first axial position is supported in the
axial direction on the base shaft and is locked against rotation via the
cam, the cam configured to be received in a valley between the two-topped
profile.

15. The hinge actuator according to claim 3, wherein the coupling ring, in
the first position, is axially moveable from a first axial position to a
second axial position.

16. The hinge actuator according to claim 10, wherein the coupling ring,
in the second position, is supported on the auxiliary coupling ring.

17. The hinge actuator according to claim 16, wherein in the second
position, the coupling ring in a second axial position is under axial
spring action in the direction of the first position and is supported on
the auxiliary coupling ring via a downwardly reaching cam.

18. The hinge actuator according to claim 10, wherein in the second
position, the auxiliary coupling ring is supported on the supporting
frame.

19. A hinge actuator comprising:a first part including first stops, the
first part comprising a base plate and including a base shaft;a second
part including second stops, the second part comprising a supporting
frame extending around the base shaft for supporting a mirror housing;an
electric drive, the first part configured for connection to the second
part via the electric drive; anda coupling provided between the first and
second parts such that in a first position the first part and the second
part are connected via the drive and can be pivoted relative to each
other manually, and in a second position the first part and the second
part are not connected via the drive and can be pivoted relative to each
other manually;wherein the first and second stops only cooperate in the
second position of the coupling in an opposite pivoting direction and are
configured to define a select or predetermined position, the first and
second stops are not active in the first position of the coupling, and
the first and second stops are only active in the second position of the
coupling;wherein the second stops are formed by a cam that is configured
or arranged on the supporting frame for traversing a path during pivoting
of the supporting frame, and at least one first stop is positioned
fixedly with respect to the base shaft; including a first pair of butting
faces of a first cam track, the first pair of butting faces positioned
fixedly with respect to the base shaft; and the first stops are formed by
the cam arranged on the supporting frame and at least one second stop
configured or arranged to be movable with respect to the base shaft;
andwherein the path in the first position is formed by the first cam
track provided on a base ring, the base ring mounted fixedly with respect
to the base shaft, and wherein the path in the second position is at
least partly formed by a second cam track, the second cam track provided
on an auxiliary ring that prohibits or impedes rotation and is axially
moveable relative to the base ring.

20. The hinge actuator according to claim 19, wherein the auxiliary ring
abuts the coupling ring.

21. A method for adjusting first and second parts of a hinge actuator
relative to each other, comprising:providing an electric drive configured
for connecting a first part to a second part, and first and second stops
that cooperate in a pivoting direction to define a select or
predetermined position;providing for a first condition in which the first
and second parts are coupled with each other by the electric drive such
that the first and second parts can pivot relative to each other with the
aid of the drive, such that the first stops are not active in the first
condition;providing for a second condition in which the first part and
the second part are not connected via the drive and the first and second
parts can be pivoted relative to each other manually, such that the first
stops are active in the second condition in an opposite pivoting
direction for defining the select or predetermined position; andadjusting
the first and second parts relative to each other.

[0002]The invention relates to a hinge actuator, including a hinge
actuator for use in connection with a mirror adjustment mechanism for a
wing mirror unit of a motor vehicle.

SUMMARY

[0003]The invention relates to a hinge actuator comprising a first part
which is configured for connection with a second part via an electric
drive, wherein the first and the second part are provided with stops
cooperating in a pivoting direction for defining a select or
predetermined position of the actuator parts with respect to each other,
wherein further a coupling is provided between the first and the second
part, so that in a first position of the coupling the first part and the
second part are connected via the drive and can be pivoted relative to
each other with the drive, and a second position in which the first part
and the second part are not connected via the drive and can be pivoted
relative to each other manually.

[0004]Such a hinge actuator is known, for instance, as used in a mirror
adjustment mechanism for a wing mirror unit of a motor vehicle. The first
part of the actuator is fixedly mounted on the motor vehicle. The second
part supports a mirror housing and can pivot relative to the first part
to the predetermined position, for instance a fold-in position to reduce
the width of the vehicle, for instance after parking, or a fold-out
position for use of the wing mirror unit under normal operating
conditions. The predetermined position is defined by the stops
cooperating in the pivoting direction, so that further pivoting is
prevented.

[0005]The two parts of the hinge actuator can be pivoted both electrically
and non-electrically, for instance manually. By the use of the coupling
between the two parts, the electric drive can be uncoupled so that a
pivoting movement of the wing mirror unit not caused by the drive, for
instance upon manual pivoting, does not force any movements of the drive,
and damage to the electric drive, such as fractures in a drive train or
defects in an electric motor, can be prevented.

[0006]It is desired to define the predetermined position of the mirror
housing so well that unintended pivoting back is prevented. As a
consequence, the influence of external forces exerted on the mirror
housing, such as air flowing along the wing mirror unit, for instance
gusts of wind or driving wind, is reduced. By the provision of an
additional pair of stops which cooperate in the predetermined position in
an opposite pivoting direction, this problem could be mitigated. In order
to enable electrical pivoting back from the predetermined position, the
reaction force caused by the additional pair of stops should not exceed a
predetermined level when pivoting electrically, since the drive must be
able to overcome the reaction force.

[0007]In addition, however, it is desirable that the mirror housing, upon
manual adjustment to the predetermined position, be secured in such a way
that a clearly sensible coupling or `click` can be felt and that the
force that is needed to adjust the mirror housing further in the pivoting
direction is of the same order of magnitude as the required force for
pivoting the mirror housing in a direction opposite to the pivoting
direction. To realize this, the reaction forces caused by the stops
should be of the same order of magnitude in both directions. However, the
electric drive then cannot adjust the mirror housing from the
predetermined position, unless unacceptably powerful and costly electric
motors are used, or the reaction forces caused by the stops are so slight
that upon manual adjustment no resistance of significance is sensed.

[0008]An object of the invention is to provide a hinge actuator of the
type mentioned in the opening paragraph hereof, in which, while
preserving the advantages, the disadvantages mentioned are avoided. An
object of the invention is to obtain a hinge actuator where, in the case
of manual operation, a clearly sensible coupling can be sensed upon the
predetermined position being reached, and where, with the aid of the
electric drive, still pivoting movement from the predetermined position
in the opposite pivoting direction is possible. To that end, the first
and the second part of the hinge actuator are furthermore provided with
stops only cooperating in the second position of the coupling in an
opposite pivoting direction, for defining the predetermined position.

[0009]As the stops cooperating in the opposite pivoting direction are only
active in the second position of the coupling, in which the first part
and the second part are not connected via the drive, what is achieved is
that the stops cooperating in the opposite pivoting direction, upon
manual operation can cause a reaction force which is of the same order of
magnitude as the reaction force caused by the stops cooperating in the
pivoting direction. As a result, upon manual operation, a clear coupling
is sensible. Moreover, the electric drive can still pivot the first part
relative to the second part in the opposite pivoting direction, also from
the predetermined position, since the stops cooperating in the opposite
pivoting direction are not active in the first position of the coupling,
in which the electric drive can pivot the first and second parts relative
to each other.

[0010]Also with manual operation, in case of external forces on the hinge
actuator, such as wind, undesired pivoting movement is prevented, since a
powerful coupling in the predetermined position has been obtained.

[0011]Preferably, the first part of the hinge actuator comprises a base
plate, provided with a base shaft, while the second part comprises a
supporting frame extending around the base shaft for supporting a mirror
housing, so that the hinge actuator can be used in a mirror adjustment
mechanism for a wing mirror unit of a motor vehicle.

[0012]By designing the coupling with a coupling ring which is
disengageably rotation-coupled and axially movable relative to the base
shaft, the first and the second position can be defined in a relatively
simple manner. The coupling ring can, for instance, be disengageably
rotation-coupled with the base shaft by means of a cam construction which
permits a pivoting movement upon the occurrence of an external couple
greater than a pre-set level. Due to the fact that the rotation coupling
of the coupling ring then disengages, the coupling ring also moves
axially from a first axial position which defines the first position to a
second axial position which defines the second axial position. When upon
pivoting of the first part relative to the second part of the hinge
actuator the coupling re-engages, the coupling ring moves back again to
the first axial position. Of course, for reliably defining the axial
positions of the coupling ring, also other disengageable constructions
can be used, such as, for instance, roller elements in guide tracks.

[0013]By designing the stops cooperating in the opposite pivoting
direction in such a way that the occurring reaction forces are in the
same order of magnitude as the reaction forces occurring upon cooperation
of the stops in the pivoting direction, what is achieved is that upon
manual adjustment of the hinge actuator a clear coupling can be sensed
upon the predetermined position being reached. The force that is needed
for pivoting further or back is then in the same order of magnitude.

[0014]Advantageously, the hinge actuator can be provided with a switch-off
mechanism for switching off the drive, whereby the force needed to
overcome the stops cooperating in the opposite pivoting direction is in
the same order of magnitude as the force at which the drive is switched
off by the switch-off mechanism. What is thereby achieved is that the
electric drive upon the predetermined position being reached, switches
off automatically, so that the drive is not unduly loaded and premature
wear is prevented. Since the required force for switching off is tuned to
the same order of magnitude as the force that is required to overcome the
stops cooperating in the opposite pivoting direction with manual
operation, the user will upon manual adjustment of the hinge actuator
experience a clear coupling upon the predetermined position being
reached. As desired, the required force for removing the coupling is then
of the same order of magnitude in both directions.

[0015]Preferably, the cooperating stops are formed by at least one cam
which is arranged on the supporting frame for traversing a path during
the pivoting movement of the supporting frame, and at least one first
stop positioned fixedly with respect to the base shaft, and wherein the
stops cooperating in an opposite pivoting direction are formed by the cam
which is arranged on the supporting frame and at least one second stop
arranged so as to be axially movable with respect to the base shaft. In
this way, the cam on the supporting frame cooperates elegantly with both
the first stop which prevents pivoting in the pivoting direction, and the
second, movable stop which prevents pivoting movement in the opposite
pivoting direction when the coupling is in the second position.

[0016]The invention also relates to a method for adjusting two parts of a
hinge actuator relative to each other.

[0017]Further advantageous embodiments of the invention are represented in
the subclaims.

[0018]The invention will be further elucidated on the basis of exemplary
embodiments which are represented in the drawing. In the drawings:

[0019]FIG. 1 is a first perspective view of a hinge actuator according to
the invention in disassembled condition;

[0020]FIG. 2 is a second perspective view of the hinge actuator of FIG. 1;

[0021]FIG. 3 is a perspective view of a base ring and an auxiliary ring of
the hinge actuator of FIG. 1;

[0022]FIG. 4 is a perspective view of a gear wheel and a base flange of
the hinge actuator of FIG. 1;

[0023]FIG. 5 is a schematic perspective view of an alternative embodiment
of the hinge actuator in disassembled condition;

[0024]FIG. 6 is a schematic perspective view of the hinge actuator of FIG.
5 in assembled condition with the coupling in the first position; and

[0025]FIG. 7 is a schematic perspective view of the hinge actuator of FIG.
6 in assembled condition with the coupling in the second position.

[0026]The figures are only schematic representations of preferred
embodiments of the invention. In the figures, the same or corresponding
parts are indicated with the same reference numerals.

[0027]FIGS. 1 and 2 show a preferred embodiment of a hinge actuator 1. The
hinge actuator 1 has a first part, designed as a base part 2, and a
second part, designed as a supporting frame 3, which parts can pivot
relative to each other. The base part 2 can be fixedly connected to a
motor vehicle, and has a base flange 4 on which a fixed base shaft 5 is
arranged. The base shaft 5 extends along a geometric pivoting axis A of
substantially upstanding orientation. The supporting frame 3 is built up
from modules fixedly attached to each other and extends around the base
shaft 5 and can support a mirror housing which accommodates a mirror
glass, so that the whole can serve as a wing mirror unit of a motor
vehicle. During pivoting of the hinge actuator 1, the supporting frame 3
hinges about the base shaft 5.

[0028]Arranged on the base flange 4 is a base ring 7 which likewise
extends around the base shaft 5. The side of the base ring 7 remote from
the base flange 4 is at least partly formed as a first cam track 8 to be
traversed by a cam 9 which is fixedly attached to the supporting frame 3
via a cam ring 10. The cam track 8 comprises a substantially planar
portion which is bounded at the ends by two inclined butting faces 8a, 8b
which form stops cooperating with the cam 9 in a pivoting direction for
defining a predetermined position of the actuator parts relative to each
other, such as a fold-in position of the wing mirror unit which is
suitable for performing parking maneuvers and a fold-out position for
normal use of the motor vehicle in traffic.

[0029]The supporting frame 3 accommodates an electric motor, not shown,
and a drive train coupled thereto, which constitute the drive of the
hinge actuator. The drive train is further adapted to be coupled with the
coupling ring designed as gear wheel 12, which constitutes a coupling
between the drive and a driven part of the actuator 1. The gear wheel 12
encloses the base shaft 5 and is arranged so as to be axially movable
relative thereto and further, in a first position situated near the base
flange 4, restrained from rotation relative to the base shaft 5. With the
aid of a biased spring element, not shown, the gear wheel 12 is driven in
the direction of the base flange 4. The gear wheel 12 is in engagement
with an output part of the drive train, so that the hinge actuator 1 can
be adjusted with the drive.

[0030]During manual operation of the hinge actuator 1, the lock against
rotation of the gear wheel 12 with respect to the base shaft 5 is
disengaged by the externally applied force, for instance by uncoupling a
cam construction 11 arranged between the base flange 4 and the gear wheel
12, as shown in more detail in FIG. 4. The cam construction 11 comprises
at least one cam 11a and a cam track lib which are respectively provided
on a flange ring 4a which is restrained from rotation relative to the
base flange 4, and on the gear wheel 12, or vice versa. As a result, the
gear wheel 12 moves axially, against the spring action of the spring
element, from the first position to a second position, situated farther
from the base flange 4, in which the gear wheel 12 is freely rotatable
relative to the base shaft 5. In the second position of the gear wheel
12, the supporting frame 3 can be manually pivoted relative to the base
shaft 5. This enables a manual pivoting of the wing mirror unit relative
to the motor vehicle without forcing movements of the drive. Upon
subsequent switching on of the electric drive, the gear wheel 12 couples
with the base flange 4, so that electric adjustment is possible again.

[0031]The hinge actuator 1 furthermore comprises an auxiliary ring 13
which encloses the base shaft 5 and, under spring action of the spring
element, abuts against the gear wheel 12. The auxiliary ring 13 is shown
in more detail in FIG. 3 and, with the aid of cams 14 and recesses 15, is
axially movable, though restrained from rotation relative to the base
ring 7, so that the auxiliary ring 13 can follow the axial movements of
the gear wheel 12. The side of the auxiliary ring 13 remote from the base
flange 4 is at least partly formed as a second cam track 16 to be
traversed by the cam 9 arranged on the supporting frame 3. The second cam
track has inclined butting faces 16a, 16b, so that pivoting of the
supporting frame 3 from the predetermined position in the opposite
pivoting direction is prevented.

[0032]When the gear wheel is in the first position, the hinge actuator 1
can be adjusted with the aid of the electric drive. The cam 9 of the
supporting frame 3 then traverses a path which is defined by the first
cam track 8, since the second cam track cannot come into contact with the
cam 9 in the first position of the gear wheel 12. Upon reaching a butting
face 8a, 8b of the first cam track 8, the cam 9 forms therewith a pair of
stops cooperating in the pivoting direction, causing a reaction force
whereby the electric motor 10 switches off in the predetermined position.
The hinge actuator can pivot back electrically by activating the electric
motor 10 in the opposite pivoting direction.

[0033]As described above, manual adjustment of the actuator is possible by
bringing the gear wheel 12 in the second position, as a result of which
the electric drive is uncoupled. The gear wheel 12 further pushes the
auxiliary ring 13 in the direction directed away from the base flange 4,
so that the second cam track 16 can also limit the path of the cam 9.
Upon manual pivoting of the hinge actuator 1, the cam 9 will again form,
together with a butting face 8a, 8b of the first cam track 8, a pair of
stops cooperating in the pivoting direction, thereby preventing further
pivoting in the pivoting direction. The occurring reaction forces are a
signal to the user that further pivoting is probably undesired, because a
position which is desired for the user of the motor vehicle has already
been obtained or because further pivoting is not possible in terms of
construction technique. Also pivoting back is now prevented by the cam 9
which, together with a butting face 16a, 16b of the second cam track 16,
forms a pair of stops cooperating in the opposite pivoting direction. As
a result, the person performing the pivoting movement experiences a
clearly noticeable coupling in the predetermined position of the
supporting frame 3 with respect to the base shaft 5. Owing to the
specific shape and dimensions of the butting faces 8a, 8b, 16a, 16b, the
required force to overcome the two pairs of cooperating stops is in the
same order of magnitude. The cam 9 is oriented so broadly that
cooperation with the butting faces of both the first and the second cam
track 8, 16 is possible. Instead of one integrated cam 9, however, two
cams may be arranged which, if desired, can include an angle relative to
each other. Also in the case of other pivoting movement of the hinge
actuator, not caused by the drive, for instance upon contact with a
foreign object, such as a pillar, the above-outlined interplay of forces
occurs.

[0034]The hinge actuator 1 furthermore comprises a current limiting
circuit which serves as a switch-off mechanism. When, upon the supporting
frame 3 and the base shaft 5 reaching the predetermined position, the
electric current in the electric motor increases in order to generate a
sufficient couple, the current limiting circuit switches off the electric
motor at a predetermined current intensity, so that damage to the
electric motor is prevented. The butting faces 16a, 16b of the second cam
track 16 are so designed that overcoming the reaction forces caused with
the cam 9 in the predetermined position of the hinge actuator would
generate such a large current in the electric motor that the current
limiting circuit would enter into operation and switch off the electric
motor.

[0035]Optionally, the hinge actuator may furthermore be provided with a
resilient ring for driving the auxiliary ring in the direction of the
base flange in order to prevent stops being able to cooperate in the
opposite pivoting direction when the first and second part of the
actuator are connected with each other via the drive.

[0036]FIGS. 5, 6 and 7 show an alternative preferred embodiment of the
hinge actuator 101. The hinge actuator 101 has a first part, designed as
a base part 102, and a second part, designed as a supporting frame 103,
which parts can pivot relative to each other. The base part 102 can be
fixedly connected to a motor vehicle, and has a base flange 104 on which
a fixed base shaft 105 is arranged. The supporting frame 103 is built up
from modules fixedly mounted on each other, extends around the base shaft
105 and can support a mirror housing in which a mirror glass is included,
so that the whole can serve as a wing mirror unit of a motor vehicle.
During pivoting of the hinge actuator 101, the supporting frame 103
hinges about the base shaft 105.

[0037]Formed on the base flange 104 is a cam track 108 which can be
traversed by a cam 109 which is fixedly mounted on the supporting frame
103. In the figure, for the sake of clarity, this part of the base frame
is represented as a separate cam ring 110. It will be clear that the cam
ring 110 may be integrated with the bottom of the supporting frame 103.
The cam track 108 comprises a substantially planar portion which is
bounded at the ends by an inclined butting face 108a which cooperates in
the pivoting direction indicated by the arrow P with a corresponding stop
surface 109a of the cam 109. The stop surfaces 108a, 109a form
cooperating stops for defining in a first pivoting direction a
predetermined position of the actuator parts 102,103 with respect to each
other. In the figure, this is represented as a fold-out position of the
wing mirror unit during normal use of the motor vehicle in traffic, which
is defined in the fold-out direction.

[0038]Included in the supporting frame 103 is an electric motor 120 with a
drive train 121 coupled to it, which constitute the drive of the hinge
actuator. The output part of the drive is formed as a gear wheel 112
which is arranged as a coupling ring around the base shaft 105. The gear
wheel 112 and the base shaft 105 together constitute a coupling 111 so
that, in the first position of the coupling, the base part 102 and the
supporting frame 103 are connected via the drive and can be pivoted
relative to each other with the drive, and in a second position, the base
part 102 and the supporting frame 103 are not connected via the drive and
can be pivoted relative to each other manually.

[0039]The gear wheel 112 encloses the base shaft 105 and is so arranged as
to be axially movable relative thereto. In a first position, situated
axially closer to the base flange 104, the gear wheel 112 is further
restrained from rotation, that is, rotation-coupled with respect to the
base shaft 105.

[0040]During application of an external force on the hinge actuator 101,
as in the case of manual operation, the lock against rotation of the gear
wheel 112 relative to the base shaft 105 can be disengaged by uncoupling
the coupling 111 between the gear wheel 112 and the base shaft 105.

[0041]To that end, the coupling 111 comprises, on the one hand, three
two-topped profiles 122 arranged on the circumference of the base shaft
105 and, on the other hand, cams 123 reaching downwards with respect to
the gear wheel 112 for cooperation with the two-topped profiles. In the
first position of the coupling, the gear wheel 112, in a first axial
position, is supported axially on the base shaft 105 and locked against
rotation in that the cams 123 are each lodged in valleys 124 between tops
125 of the two-topped cam track profiles 122. In the first position of
the coupling 111, the gear wheel 112 is axially movable from a first
axial position, in an axial direction directed away from the base flange
104, to a second axial position.

[0042]When under the influence of an external force the supporting frame
103 is rotated about the base shaft 105, the gear wheel 112 is carried
along by the drive train 121, and the cams 123 are guided axially upwards
via the flanks of the tops 125 contiguous to the valley 124. After
passing the tops 125, the cams will be guided downwards under the action
of a coil spring 106 arranged around the base shaft 105, along the
inclined flanks of the two-topped profile 122 remote from the valleys,
down onto a top surface of an auxiliary coupling ring 126 arranged around
the base shaft 105 between the gear wheel 112 and the supporting frame
103, so that the gear wheel 112 reaches a second axial position in which
it is freely rotatable relative to the base shaft 105. The function of
the auxiliary coupling ring 126 will be further elucidated hereinafter.

[0043]The coupling 111 enables a manual pivoting of the wing mirror unit
relative to the motor vehicle without forcing movements of the drive.

[0044]By the use of the coupling 111, the supporting frame 103 can
therefore be pivoted around the base part through both electric drive and
manual operation. The fold-out position is then defined in a first
pivoting direction, i.e. towards the fold-out position, by cooperation of
the stop surfaces 708a, 709a.

[0045]During pivoting in the first direction towards the fold-out
position, the electric operation can be switched off with the aid of a
current limiting circuit 130. When, upon reaching the predetermined
position of the supporting frame 103 through cooperation of the stops
108a, 109a, the electric current in the electric motor increases, the
current limiting circuit 130 switches off the electric motor at a
predetermined current intensity, thereby preventing damage to the
electric motor or drive train.

[0046]Under the influence of an external force, the cooperating stops
108a, 109a can be overcome against the action of the spring 106, so that
the base frame 103 can be pivoted further in the direction of the arrow P
to a fold-over position. The supporting frame 103 can then be pivoted
back both with the aid of the electric drive and manually.

[0047]When the first and the second part are connected via the drive, the
fold-out position is defined in the opposite pivoting direction in that
the drive prevents pivoting.

[0048]For defining the fold-in position in the case of manual operation in
the opposite pivoting direction, i.e. in the inward pivoting direction,
the hinge actuator 101 is equipped with an auxiliary coupling ring 126
which is arranged around the base shaft 105. The auxiliary coupling ring
126 is arranged between the gear wheel 112 and the supporting frame 103.
The auxiliary coupling ring 126 and the mirror supporting frame 103 are
provided with auxiliary stops 127,128 cooperating only in the second
position of the coupling 111 in the opposite pivoting direction. These
auxiliary stops therefore constitute the stops for defining the
predetermined position in the opposite pivoting direction. The auxiliary
coupling ring 126 is arranged around the base shaft 105 so as to be
axially movable and rotation-coupled. The auxiliary stops 128 are formed
by stop surfaces 128a on two cam tracks 128' which are provided on the
undersurface of the auxiliary coupling ring 126. The auxiliary stops 127
are formed by stop surfaces 127a which are provided on two upwardly
reaching cams 127' on the supporting frame 103. As will be elucidated
hereinafter, the cam tracks 128' and the cams 127' cooperate to define
the fold-out position in the fold-in direction when as a result of an
externally applied force the coupling is in the second position, and the
cams 123 of the gear wheel 112 therefore rest on the top surface of the
auxiliary coupling ring 126. It will be clear that the cams 127' and the
cam tracks 128 can also be interchanged.

[0049]The hinge actuator 101 further comprises an intermediate ring 129,
arranged around the base shaft, which is under axial action of the spring
106. In a first position of the coupling 111, the intermediate ring 129
is supported directly on the supporting frame 103. In the second position
of the coupling 111, the upper surface of the gear wheel 112 is in the
second position, which is situated axially farther from the base flange
104 than the first position. The intermediate ring 129 is then supported
on the upper surface of the gear wheel 112. As a result, when the gear
wheel 112, as described above, has been brought into the second position
upon manual pivoting of the supporting frame 103, the auxiliary coupling
ring 126 will become subject to spring action. What is thus achieved is
that in the first position of the coupling, in which the gear wheel 112
is supported on the base shaft 105 while the auxiliary coupling ring is
freely movable with limited travel, the cam tracks 128' on the auxiliary
coupling ring 126 do not cooperate under spring action with the cam
tracks 127'. As a result, the stop surfaces 127a, 128a will not cooperate
as stops during electrically-driven inward pivoting from the fold-out
position. Upon electrically-driven inward pivoting, the auxiliary
coupling ring 126 will be moved axially upwards and permit pivoting
without resistance of significance.

[0050]What can optionally be achieved by providing a slight friction
between the auxiliary coupling ring 126 and the base shaft 105, is that
the stop surfaces 127a, 128a are axially spaced apart during normal
(electric) operation and hence do not touch upon being pivoted relative
to each other.

[0051]In the second position of the coupling, however, the auxiliary
coupling ring 126 is under downward spring action via the gear wheel 112,
which is now in the second position. The auxiliary coupling ring 126
transmits the spring force to the supporting frame 103, viz. in that the
auxiliary cam 127' is pressed onto the auxiliary cam track 128'. When the
supporting frame is pivoted further to the predetermined position, the
auxiliary cam 127' will follow the auxiliary cam track 128' and be guided
along auxiliary stop surface 128a to a higher supporting surface 128'' of
the cam track 128'.

[0052]As a result, the auxiliary coupling ring 126, together with the gear
wheel 112, will undergo a downward movement, i.e. towards the base flange
104. In the process, however, the two preferably remain under spring
action. The downward movement is limited in that the stop surfaces 127a
and 128a cooperate in the opposite pivoting direction, and also in that
stop surfaces 127a of auxiliary cams 127' and supporting surfaces 128''
of the cam tracks 128'cooperate, so that eventually the predetermined
position is defined. As the fold-out position is approached during
folding out, this will be experienced by the pivoting person as a clear
`click`.

[0053]After a manual pivoting to the fold-out position as described above,
then, upon manual operation in the opposite pivoting direction, first the
stops 127, 128 will have to be overcome against the action of the spring
106, so that a clear `click` can be felt again. The auxiliary coupling
ring 126 is then pressed upwards, together with gear wheel 112, against
the spring action. In this way, therefore, it is possible upon manual
operation to feel a clear `click` both upon outward pivoting to the
fold-out position and upon pivoting back from the fold-out position,
while this `click` can remain absent in the case of electrical pivoting
back.

[0054]The invention is not limited to the exemplary embodiments described
here. Many variants are possible.

[0055]Thus, the coupling ring designed as gear wheel can be designed
differently, for instance as a ring which constitutes a disengageable
coupling between a driven part of the electric drive and a first or
second part of the hinge actuator.

[0056]Also, the cam may be fixed on the base ring, with butting faces
provided on the supporting frame and the auxiliary ring. The auxiliary
ring is then locked against rotation with respect to the supporting
frame. Furthermore, the cam tracks and the cam can be of eccentric or
other design.

[0057]Furthermore, the switch-off mechanism, instead of being designed as
a current limiting circuit, can also be designed with the aid of a
different mechanism, for instance with the aid of a friction coupling.

[0058]Such variants will be clear to those skilled in the art and are
understood to fall within the scope of the invention as set forth in the
following claims.